CN1745258A - Clearance regulation mechanism with locking device - Google Patents
Clearance regulation mechanism with locking device Download PDFInfo
- Publication number
- CN1745258A CN1745258A CNA200480003149XA CN200480003149A CN1745258A CN 1745258 A CN1745258 A CN 1745258A CN A200480003149X A CNA200480003149X A CN A200480003149XA CN 200480003149 A CN200480003149 A CN 200480003149A CN 1745258 A CN1745258 A CN 1745258A
- Authority
- CN
- China
- Prior art keywords
- mentioned
- tappet
- locking framework
- lever
- axis
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D65/00—Parts or details
- F16D65/38—Slack adjusters
- F16D65/40—Slack adjusters mechanical
- F16D65/52—Slack adjusters mechanical self-acting in one direction for adjusting excessive play
- F16D65/56—Slack adjusters mechanical self-acting in one direction for adjusting excessive play with screw-thread and nut
- F16D65/567—Slack adjusters mechanical self-acting in one direction for adjusting excessive play with screw-thread and nut for mounting on a disc brake
- F16D65/568—Slack adjusters mechanical self-acting in one direction for adjusting excessive play with screw-thread and nut for mounting on a disc brake for synchronous adjustment of actuators arranged in parallel
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2121/00—Type of actuator operation force
- F16D2121/14—Mechanical
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2125/00—Components of actuators
- F16D2125/18—Mechanical mechanisms
- F16D2125/20—Mechanical mechanisms converting rotation to linear movement or vice versa
- F16D2125/22—Mechanical mechanisms converting rotation to linear movement or vice versa acting transversely to the axis of rotation
- F16D2125/28—Cams; Levers with cams
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2125/00—Components of actuators
- F16D2125/18—Mechanical mechanisms
- F16D2125/20—Mechanical mechanisms converting rotation to linear movement or vice versa
- F16D2125/22—Mechanical mechanisms converting rotation to linear movement or vice versa acting transversely to the axis of rotation
- F16D2125/28—Cams; Levers with cams
- F16D2125/32—Cams; Levers with cams acting on one cam follower
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2125/00—Components of actuators
- F16D2125/18—Mechanical mechanisms
- F16D2125/58—Mechanical mechanisms transmitting linear movement
- F16D2125/64—Levers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D2125/00—Components of actuators
- F16D2125/18—Mechanical mechanisms
- F16D2125/58—Mechanical mechanisms transmitting linear movement
- F16D2125/70—Rods
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Braking Arrangements (AREA)
Abstract
A slack adjustment system for a disk brake includes a biasing member to adjust slack in a brake system. The biasing member operates independently of pressure applied to a brake actuator. A locking device secures the adjustment mechanism in place when adjustment is not necessary. Release of the locking member allows the biasing member to adjust the resting position of brake pads independent of driver applied brake pressure.
Description
Background of invention
The present invention relates to the controlling mechanism of braking device.
When brake pad or brake disc wear, the interval between this brake pad and the brake disc just increases.Because distance increases between the brake pad brake disc, just can make the braking device engagement so must be moved further brake operating mechanism.In other words, be subjected to doing the time spent at braking device, it is increasing that the gap becomes, and this makes braking device become not too effective.In order to compensate this gap, before brake engaged, clearance adjustment mechanism moves brake pad, moves on to more close brake disc.The length of regulating load bearing part can be guaranteed the path increment of operating device unanimity, and no matter whether brake pad weares and teares.
Conventional system controlling mechanism uses suitable complicated mechanical assembly to carry out this operation.Usually adopt the added power of brake operating mechanism to drive controlling mechanism, but reduced the validity and the ability of braking device like this.
In addition, when not using braking device, controlling mechanism may displacement.This displacement may cause unwanted brake pad wear, perhaps increases the gap of braking system in addition, and this may reduce the brake operating performance.
Therefore, need provide a kind of controlling mechanism, this controlling mechanism does not increase driver's active force, and when not using braking to roll, can be subjected to reliable constraint.
Brief summary of the invention
Gap adjustment of the present invention system provides a kind of controlling mechanism, and this mechanism utilizes biasing member to come the gap of regulating system.This bias system is independent of braking and makes the added pressure work of operating device.When not needing to regulate, adopt locking framework with the controlling mechanism fix in position.In addition, the gap length of locking mechanism controls requirement.
This locking framework alternative engagement tappet or any rotatable parts that mesh with above-mentioned tappet rotate and bootlessly regulate the interval between brake pad and the brake disc to prevent tappet.With the lock bolt that tappet cooperatively interacts, when this tappet of engagement, can prevent rotation.After tappet was scheduled to move, this lock bolt and tappet were thrown off.Unclamping locking framework just can make this tappet rotate.This biasing member is mounted to, and when not retardation motion of Lock Part, can mesh and rotate tappet.This biasing member is not rely on to act on brake operating mechanism upward pressure and with this biasing member on the rotating force effect thrust assemblies.This biasing member can be spring, power motor, pneumatic motor etc.
Therefore, the invention provides that a kind of driver of not relying on acts on the braking system upward pressure and the method for regulating the gap automatically.In addition, locking device can prevent to regulate unintentionally the gap of braking system.
Brief Description Of Drawings
The technician can obviously find out various feature and advantage of the present invention according to following present DETAILED DESCRIPTION OF THE PREFERRED.Following brief description is with the accompanying drawing that describes in detail:
Fig. 1 is a cross-sectional side view, and the brake assemblies with gap adjustment of the present invention system is shown;
Fig. 2 is the cross-sectional plan views of brake assemblies;
Fig. 3 is the cross-sectional plan views of gap adjustment of the present invention system, and the tappet that moves forward a segment distance is shown, and this segment distance equals the degree of tightness amount of requirement, and lock bolt is just in time thrown off with rotatable parts among the figure;
Fig. 4 is the cross-sectional plan views of gap adjustment of the present invention system, all parts is shown all is positioned at the position that braking device is fully acted on;
Fig. 5 is a cross-sectional plan views, and the gap adjusting mechanism that is positioned at locked position of the present invention is shown,
Fig. 6 is the sectional view end elevation of rotatable parts and tappet gear, and preferred rotating manner is shown.
DETAILED DESCRIPTION OF THE PREFERRED
Fig. 1 illustrates disc braking assembly 10, and this assembly adopts gap adjusting mechanism 12 of the present invention.This disc braking assembly has base 11, and this base surrounds inner member, and supporting is by the load of these parts generations.When driver's operation braking device (not shown), input load (L schematically illustrates with arrow) just passes on the bar thick stick 14 by the hole on the base 11 16, and this lever 14 is supported by base 11 rotationally by bearing support 18.This lever rotates around lever axis 20.That is, this lever 14 rotates around lever axis 20 clockwise, as shown in Figure 1.The bottom of this bar is a spill, thereby can keep columniform roller 22.This roller 22 is eccentric with respect to the center of rotation of lever 14.That is, the axis 24 of roller moves along one section arc around lever axis 20.
Input load L makes lever 14 rotate around lever axis 20, and roller 22 is moved (lever 14 accessible extreme strokes are represented in the position that is shown in dotted line) along one section arc around lever axis 20.The eccentric motion of roller 22 can mesh one or more thrust assemblies 26, and applies load to this thrust assemblies 26, makes thrust assemblies 26 vertically to move apart lever 14 by support 61 guiding.Preferred embodiment shown in Figure 2 comprises two thrust assemblies 26.This thrust axis of determining perpendicular to lever axis and roll axis 20 and 24 27 that moves.Thrust assemblies 26 makes brake pad 28 engagements along the axial motion of thrust axis 27 by push plate 62.These brake component 28 engagement brake discs 29.When driver's take-off the brake device, the input load of operating device just reduces, and Returnning spring draws driving thrust assemblies 26 is turned back to the origin-location.Therefore lever 14 and roller 22 are also got back to the origin-location.When not applying input load L, Returnning spring 31 constrains in the origin-location with thrust assemblies 26, roller 22 and lever 14.
With reference to Fig. 2, locking framework 42 selectivity mesh the gear on the tappet screw 64, thereby can prevent the interval between tappet screw 64 rotations and unhelpful adjusting brake pad 28 and the brake disc 29.Do not done the time spent with the rotatable parts 48 ground lock bolt 54 that cooperatively interacts at braking device, can prevent rotation, but be subjected to doing the time spent at braking device, thrust assemblies 26 can move the distance less than predetermined crack, workshop.Lock bolt 54 is contained on the link rod 56, and this link rod can be a bar etc., is contained on the lever 14.
Do not done the time spent at braking device, perhaps moved past less than predetermined degree of tightness amount and between the normal brake application moving period when regulating in thrust assemblies 26, these rotatable parts 48 and tappet screw 64 can be by locking framework 42 lockings, and can not rotate.When nibbling locking framework 42, rotatable parts 48 and tappet screw 64 can not be rotated.Act on the power on the tappet screw 64 by the rotation of lever 14, axially pushing thrust assemblies 26 to brake disc 29 along pushing force axis 27 along axis.This locking framework 42 is made up of lock bolt 54, this lock bolt is driven by lever 14 through link rod 56, this locking framework can be with respect at the gear movement of rotatable parts 48 outsides (as shown in Figure 3, make it along the axial-movement that is parallel to thrust axis 27, perhaps can make it radially move apart this thrust axis) by reconfiguring link rod 56.The geometrical shape of link rod 56 is determined the point that lock bolt 54 is thrown off.When the predetermined gap eliminated between brake pad 28 and the brake disc 29, being out of gear on lock bolt 54 and the rotatable parts 48.Simultaneously, load begins to act on the brake pad 28 by thrust assemblies 26.This load will produce friction torque between tappet nuts 63 and tappet screw 64, relatively rotate thereby prevent, thereby to prevent and be subjected to regulating as the time spent at braking device, as shown in Figure 4.When the take-off the brake device, all parts all turn back to its original position by Returnning spring 31, and any adjustment of thrust assemblies 26 length can not take place.
When brake pad 28 abrasions, the gap between brake pad 28 and the thrust assemblies 26 will increase, and thrust assemblies 26 must move bigger distance along thrust axis 27, just can make brake pad 28 contact brake discs 29.In order to compensate the wearing and tearing of brake pad 28, must regulate tappet screw 64, increase the total length of thrust assemblies.Thus, between brake pad 28 and brake disc 29, keep constant gap always.
With reference to figure 5, can utilize regulating system 12 of the present invention to regulate the gap of brake assemblies 10.When unclamping locking framework 42, rotatable parts 48 and tappet screw 64 just can be rotated.Biasing member 44 is contained on the support 61, and the bias voltage moment of rotation is acted on the rotatable parts 48.Biasing force axis 46 preferably is parallel to thrust axis 27, and staggers with it, but can be positioned at any position or the angle of support 11 the insides or outside, in this position or angle, and still can be directly and be engaged in tappet screw 64 indirectly.This biasing member 48 is helical spring preferably, but can be other forms, for example electric notor, pneumatic motor etc.Rotatable parts 48 are installed near biasing member 44, and can be driven by biasing member 44, rotate around bias voltage axis 46 along first sense of rotation 50.Rotatable parts 48 preferably utilize the gear on the gear engagement tappet screw 64 on the tappet.But also can adopt other geared assembly.Tappet screw 64 is rotated around thrust axis 27 along second sense of rotation 52, and promptly rotatable parts 48 rotate along counterclockwise direction, and this rotation makes tappet screw 64 rotate along up time nail direction again, as shown in Figure 5.These rotatable parts 48 are gear preferably.
The rotation of tappet screw 64 makes tappet nuts 63 shift to system pad 28 thrust assemblies 28 that extends thus, and reduces the gap.Be subjected to doing the time spent at the braking rolling device, thrust assemblies 26 has moved past after the predetermined gap, and this lock bolt 54 is thrown off with rotatable parts 48.If there is excessive gap, then tappet screw can freely be rotated, and its clockwise direction is driven, the thrust assemblies 26 that can extend thus, and reduce the gap.When thrust assemblies, brake pad 28 and brake disc 29 are in contact condition, and when adding load by thrust assemblies 26, between tappet nuts 63 and tappet screw 64, just produce friction torque, relatively rotate, thereby prevent the adjustment that is subjected to doing the time spent at the effect braking device thereby prevent.Preferred sense of rotation as shown in Figure 6.
When the take-off the brake device, if when thrust assemblies 26 is removed all loads, still there is excessive gap, then will further rotate rotatable parts 48 and tappet screw 64, as leading portion explanation, be rotated further, equal predetermined gap up to the stroke of thrust assemblies.Lock bolt 54 is engaged on the gear on the rotatable parts 58 again subsequently, prevents further thus and rotates, thereby prevent to regulate the length of thrust assemblies 26.
Above-mentioned explanation only example illustrates principle of the present invention.By above-mentioned explanation, can carry out various remodeling of the present invention and change.The preferred embodiments of the present invention have been described, the preferred embodiments of the present invention have been described, made those of ordinary skill obviously to find out, some remodeling belong to scope of the present invention.Therefore, should be understood that within the scope of the appended claims that the present invention can implement to be different from the above-mentioned mode that specifies.For this reason, following claims be should study, true scope of the present invention and main points determined.
Claims (21)
1. the gap adjustment system of a Disk brake apparatus comprises:
Lever is mounted to and can rotates around lever axis;
Biasing member, being mounted to can be around the biasing force rotational, the above-mentioned lever axis of this biasing force axis normal;
Rotatable parts are contained on the above-mentioned biasing member, respond above-mentioned biasing member, above-mentioned biasing member along first direction around above-mentioned biasing force axis bias voltage rotatable parts;
At least one tappet, this tappet is engaged in above-mentioned rotatable parts, so that rotate around the thrust axis that is parallel to above-mentioned biasing force axis in second direction;
Be contained in the locking framework on the above-mentioned lever, so that above-mentioned at least one tappet of selectivity engagement prevents its rotation.
2. the system as claimed in claim 1 is characterized in that, above-mentioned biasing force axis and above-mentioned thrust axis are setovered.
3. the system as claimed in claim 1 is characterized in that, above-mentioned rotatable parts and above-mentioned at least one tappet comprise gear.
4. system as claimed in claim 3 is characterized in that above-mentioned locking framework is connected in the tooth of said gear.
5. the system as claimed in claim 1 is characterized in that, above-mentioned locking framework responds above-mentioned lever and throws off around above-mentioned lever axis rotation and with above-mentioned tappet.
6. system as claimed in claim 5 is characterized in that threaded rotating shaft responds the disengagement of above-mentioned locking framework and above-mentioned tappet, and by above-mentioned tappet it is rotated around above-mentioned thrust axis.
7. system as claimed in claim 6 is characterized in that, when braking device fully meshes, can prevent that above-mentioned tappet from rotating.
8. system as claimed in claim 6 is characterized in that, responds the above-mentioned rotation that threaded shaft is arranged, and the thrust assemblies that can extend is along the length of above-mentioned thrust axis.
9. system as claimed in claim 8 is characterized in that, utilizes above-mentioned push plate and contacting that a system is filled up, and can prevent the rotation of above-mentioned tappet.
10. the system as claimed in claim 1 is characterized in that, above-mentioned biasing member comprises spring.
11. the system as claimed in claim 1 is characterized in that, above-mentioned biasing member comprises helical spring.
12. the system as claimed in claim 1 is characterized in that, above-mentioned locking framework is a lock bolt.
13. the system as claimed in claim 1 is characterized in that, a bar supports above-mentioned locking framework, and makes above-mentioned locking framework be fixed in above-mentioned lever.
14. the system as claimed in claim 1 is characterized in that, a cam supports above-mentioned locking framework, and makes above-mentioned locking framework be fixed in above-mentioned lever.
15. the system as claimed in claim 1 is characterized in that, two tappets are arranged.
16. a disc brake gap adjustment method may further comprise the steps:
A) along first direction bias voltage rotatable parts;
B) locking framework and tappet are thrown off, make rotatable parts drive this tappet along second direction;
C) rotation of response tappet, lengthening thrust assemblies, thereby the gap of reducing braking device.
17. method as claimed in claim 16 is characterized in that, above-mentioned steps b) also comprise and make above-mentioned locking framework slide into disengaged orientation from the engaging position.
18. method as claimed in claim 16 is characterized in that, above-mentioned steps a) also comprises and makes the engagement of rotatable parts and tappet.
19. method as claimed in claim 16 is further comprising the steps of:
D) push plate is contacted with brake pad, prevent that tappet from rotating.
20. method as claimed in claim 17 is characterized in that, above-mentioned steps b) also comprise the rotation that utilizes lever, make above-mentioned locking framework slippage to above-mentioned disengaged orientation.
21. method as claimed in claim 16 is characterized in that, above-mentioned steps b) also comprise and make locking framework turn to disengaged orientation from the engaging position.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US10/355,511 US6955246B2 (en) | 2003-01-31 | 2003-01-31 | Rapid take up and vibration proof adjuster mechanism |
| US10/355,511 | 2003-01-31 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN1745258A true CN1745258A (en) | 2006-03-08 |
Family
ID=32770555
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNA200480003149XA Pending CN1745258A (en) | 2003-01-31 | 2004-02-02 | Clearance regulation mechanism with locking device |
Country Status (6)
| Country | Link |
|---|---|
| US (1) | US6955246B2 (en) |
| EP (1) | EP1595087B1 (en) |
| JP (1) | JP2006516704A (en) |
| CN (1) | CN1745258A (en) |
| DE (1) | DE602004010370T2 (en) |
| WO (1) | WO2004070226A1 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104428555A (en) * | 2012-07-31 | 2015-03-18 | 相信Brake株式会社 | Disk brake for vehicle having gear connection |
| CN112413007A (en) * | 2019-08-23 | 2021-02-26 | 比亚迪股份有限公司 | Disc brake and vehicle |
Families Citing this family (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7931129B2 (en) | 2003-01-31 | 2011-04-26 | Arvinmeritor Technology, Llc | Rapid take up and vibration proof adjuster mechanism |
| DE10307734B3 (en) * | 2003-02-24 | 2004-09-30 | Knorr-Bremse Systeme für Nutzfahrzeuge GmbH | Disc brake for a vehicle, in particular a commercial vehicle |
| DE102004042574A1 (en) * | 2004-09-02 | 2006-03-30 | Knorr-Bremse Systeme für Nutzfahrzeuge GmbH | Disc brake, in particular for commercial vehicles |
| DE102004045951B4 (en) * | 2004-09-22 | 2008-02-28 | Knorr-Bremse Systeme für Nutzfahrzeuge GmbH | Method for adjusting the clearance of a disc brake |
| CN101103209A (en) * | 2004-11-17 | 2008-01-09 | 布赖恩·安东尼·泡森 | Mechanical disc brake assembly |
| CN100383428C (en) * | 2005-12-22 | 2008-04-23 | 江苏恒力制动器制造有限公司 | Double thrust disc and double regulating caliper type pneumatic brake device capable of self-regulating braking clearance |
| DE102009018223A1 (en) * | 2009-04-21 | 2010-11-11 | Knorr-Bremse Systeme für Nutzfahrzeuge GmbH | Pneumatically or electromechanically actuated disc brake |
| DE102009033394A1 (en) * | 2009-07-16 | 2011-01-27 | Knorr-Bremse Systeme für Nutzfahrzeuge GmbH | Pneumatically or electromechanically actuated disc brake |
| WO2014021646A1 (en) | 2012-07-31 | 2014-02-06 | 상신브레이크 주식회사 | Disk brake for vehicle comprising guide pin |
| DE102016116793A1 (en) * | 2016-09-08 | 2018-03-08 | Knorr-Bremse Systeme für Nutzfahrzeuge GmbH | Brake caliper of a disc brake |
| JP6732712B2 (en) * | 2017-09-29 | 2020-07-29 | 日立オートモティブシステムズ株式会社 | Electric disc brake |
| US10677303B2 (en) | 2018-02-06 | 2020-06-09 | Bendix Spicer Foundation Brake Llc | Disc brake wear adjuster |
Family Cites Families (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4154321A (en) | 1977-03-14 | 1979-05-15 | Wagner Electric Corporation | Cam actuated disc brake |
| US4499976A (en) | 1983-06-16 | 1985-02-19 | Rockwell International Corporation | Slack adjuster for a disc brake |
| JP2511994B2 (en) | 1987-08-04 | 1996-07-03 | 曙ブレーキ工業株式会社 | Automatic gap adjustment device for disk brake |
| DE4231560C2 (en) * | 1992-09-21 | 2002-07-11 | Perrot Bremse Gmbh Deutsche | Actuator for a sliding caliper disc brake |
| DE4308704A1 (en) | 1993-03-18 | 1994-09-22 | Knorr Bremse Ag | Air operated disc brake |
| DE4334914A1 (en) * | 1993-10-13 | 1995-04-20 | Knorr Bremse Systeme | Air operated disc brake |
| US5819884A (en) * | 1994-01-18 | 1998-10-13 | Lucas Industries Public Limited Company | Clamping device of a disc brake, especially for use with heavy commercial vehicles |
| SE505339C2 (en) | 1994-10-24 | 1997-08-11 | Haldex Ab | Disc brake caliper |
| US5992579A (en) | 1997-08-07 | 1999-11-30 | Meritor Heavy Vehicle Systems, Llc | Method and apparatus for detecting an improperly adjusted slack adjuster |
| GB9806542D0 (en) | 1998-03-26 | 1998-05-27 | Lucas Ind Plc | Disc brake actuator |
| SE516513C2 (en) * | 2000-05-31 | 2002-01-22 | Haldex Brake Prod Ab | Disc brake comprising a braking mechanism |
-
2003
- 2003-01-31 US US10/355,511 patent/US6955246B2/en not_active Expired - Lifetime
-
2004
- 2004-02-02 WO PCT/US2004/002899 patent/WO2004070226A1/en active IP Right Grant
- 2004-02-02 CN CNA200480003149XA patent/CN1745258A/en active Pending
- 2004-02-02 JP JP2006501127A patent/JP2006516704A/en not_active Withdrawn
- 2004-02-02 DE DE602004010370T patent/DE602004010370T2/en not_active Expired - Lifetime
- 2004-02-02 EP EP04707384A patent/EP1595087B1/en not_active Expired - Lifetime
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104428555A (en) * | 2012-07-31 | 2015-03-18 | 相信Brake株式会社 | Disk brake for vehicle having gear connection |
| CN104428555B (en) * | 2012-07-31 | 2016-12-07 | 相信Brake株式会社 | There is the disk brake for vehicle of gear linkage |
| CN112413007A (en) * | 2019-08-23 | 2021-02-26 | 比亚迪股份有限公司 | Disc brake and vehicle |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2004070226A1 (en) | 2004-08-19 |
| US6955246B2 (en) | 2005-10-18 |
| DE602004010370T2 (en) | 2008-11-13 |
| JP2006516704A (en) | 2006-07-06 |
| DE602004010370D1 (en) | 2008-01-10 |
| EP1595087B1 (en) | 2007-11-28 |
| US20040149527A1 (en) | 2004-08-05 |
| EP1595087A1 (en) | 2005-11-16 |
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| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C02 | Deemed withdrawal of patent application after publication (patent law 2001) | ||
| WD01 | Invention patent application deemed withdrawn after publication |